Envelope making means



April 5, 1966 T. F. ARONSON ETAL 3,244,045

ENVELGPE MAKING MEANS 8 Sheets-Sheet 1 Original Filed Sept. 7, 1961 INVENTORS THEODORE F. ARONSON BY FLOYD A. LYON April 5, 1966 'r F. ARONSON ETAL 3,244,045

ENVELOPE MAKING MEANS 8 Sheets-Sheet 2 Original Filed Sept. 7, 1961 INVENTORS THEODORE F. ARONSON BY FLOYD A. LYON April 1966 T. F. ARONSON ETAL 3,244,045

ENVELOPE MAKING MEANS 8 Sheets-Sheet 3 Original Filed Sept. '7, 1961 INVENTORS THEODORE F. ARONSON FLOYD A. LYON April 5, 1966 T. F. ARONSON ETAL 3,244,045

ENVELOPE MAKING MEANS Original Filed Sept. '7, 1961 8 Sheets-Sheet 4 N y? i 28 INVENTORS' THEODORE F. ARONSON BY FLOYD A. LYON ENVELOPE MAKING MEANS 8 Sheets-Sheet 5 Original Filed Sept. '7, 1961 INVENTORS THEODORE F. ARONSON BY FLOYD A. LYON FIG. 6

April 1966 T. F. ARONSON ETAL 3,244,045

ENVELOPE MAKING MEANS 8 Sheets-Sheet 6 Original Filed Sept. '7, 1961 INVENTORS THEODORE F- ARONSON BY FLOYD A. LYON April 1966 "r. F. ARONSON ETAL 3,244,045

ENVELOPE MAKING MEANS Qriginal Filed Sept. '7, 1961 8 Sheets-Sheet 7 INVENTORS THEODORE F. ARONSON BY FLOYD A. LYON April 5, 1966 T. F. ARONSON ETAL 3,244,045

ENVELOPE MAKING MEANS Original Filed Sept. '7, 1961 8 Sheets-Sheet 8 INVENTORS THEODORE F. ARONSON BY FLOYD A. LYON United States Patent 3,244,045 ENVELOPE MAKING MEANS Theodore F. Aronson, Glen Cove, and Floyd A. Lyon,

Brookville, N.Y.; said Lyon assignor to Halm Instrument Co., Inc., Glen Head, N.Y. Continuation of application Ser. No. 136,585, Sept. 7, 1961. This application May 23, 1963, Ser. No. 282,746 3 Claims. (Cl. 83-236) This invention relates to envelope making means, more particularly to means for making different size envelope blanks. More specifically the invention relates primarily to web handling and blank handling means having continuous positive control. 7

This application is a continuation of Serial No. 136,585, filed Sept. 7, 1961, now abandoned.

In envelope making it is desirable to have one machine make different size envelopes which generally requires a fairly extensive resetting of the entire machine. This is because the different size blanks require different cutting angles of the web and a realignment of the blank handling apparatus. This is due to the fact that when the cutting angle of the web is changed, the leading point of the blank is at a different angle from the direction of motion of the web.

The present invention solves these difficulties by providing the web feeding means, a pivotally adjustable reciprocating knife to cut the web at an adjustable angle, and blank handling means adapted to twist the blanks through a predetermined angle in order to feed them in alignment with a permanently set blank conveyor system. Means are also provided to vary the length of the blanks cut. The blank conveyor is arranged to feed the blanks with a positive continuous control so that they have a predetermined overlapping pattern which is useful for the future operations such as gumming the blanks, printing, etc.

Conventional apparatus does not have the blanks un d-er continuous positive control but generally slides the blanks down an inclined plane or else stacks them in a vertical stack so that they must be again separated and handled in order to perform any further operation such as gumming or printing.

The present invention cuts the blanks with an adjustable angle reciprocating knife while the web is stationary and at the same time as the cutting,-the blank is gripped by a cone roller which twists the blank a predetermined angle depending upon the cutting angle so that the blank may be fed in alignment with a permanently fixed blank takeaway conveyor system. The cone rollers have cut away portions so as not to interfere with the leading edge of the web before it is severed.

Accordingly, a principal object of the invention is to provide new and improved envelope making means.

Another object of the invention is to provide new and improved envelope making means having novel blank cutting and handling means.

Another object of the invention is to provide new and improved means for cutting blanks from webs and handling said blanks with continuous positive control.

Another object of the invention is to provide new and improved means for making adjustble size envelope blanks comprising an adjustable angle reciprocating knife.

Another object of the invention is to provide new and improved means for making adjustable size envelope blanks comprising an adjustable angle reciprocating knife, and adjustable means to grip the blanks at the instant of severing and to twist the blanks with continuous positive control through an adjustable predetermined angle in order to feed them in a predetermined overlap ping position on a permanently fixed takeaway conveyor belt system.

3,244,045 Patented Apr. 5, 1966 Another object of the invention is to provide new and improved means for cutting and feeding blanks in predetermined overlapping relation.

These and other objects of the invention will beepparent from the following specification and drawings of which:

FIGURE 1 is a perspective view of the web handling and cutting means of the invention.

FIGURE 2 is a schematic diagram illustrating the blank handling means of the invention. v 7

FIGURE 3 is a plan view of the blank handling means of the invention.

FIGURE 4 is a plan View of the drive means of FIGURE 3.

FIGURES S and 5A show detail views of the cone rollers and sector rollers.

FIGURES 6 and 7 are side elevation views of the em bodiment of FIGURES 3 and 4.

' FIGURES 8, 8A, and 9 are detail views of the cone roller mountings. 7

FIGURE 10 is a diagram illustrative of the operation of the invention.

FIGURE 1 shows a perspective view of a portion of an embodiment of the invention. All of the members are mounted in a pair of side frames F and F the frame F being cut away to show the interior constructions. The strip 1 is fed by means of an input roller'3 which is mounted between and journalled to the frame members and which is driven at constant speed. Spring loaded pressure roller 6 bears against the roller 3.

Roller 3 is driven from driven input shaft 13 by gear 16 on shaft 13 idler gear 33 rotatably mounted on the frame, which meshes with gear 16 and with change gear '34 mounted on adjustable arm 35. 'The adjustable arm 35 has adjustment slots 35a and 35b. The arm 35 is varied to accommodate different size change gears 34 to vary the speed of roller 3. Change gear 34 meshes with gear 36 mounted on the shaft of roller 3.

The strip then passes over an idler roller 7 which is adapted to oscillate up and down. The roller 7 is mounted on arms 8 and 9, the other ends of which are pivotally mounted on the shaft 10 which is connected between and to the frame members F and F An arm 11 is pivotally mounted to the frame and has a cam follower 11 which rides in an approximately eccentric groove 12' of the flywheel cam 12. The groove is cut to compensate for any inaccuracies in the linkage.

Arm 11 is connected to roller 7 by link 5 which is pivotally connected at one end to the arm 8 and at its other end to the arm 11 by means of the adjustable pin and slot connection 5', a suitable clamp being provided to lock the adjustment. This adjustment varies the travel of the idler roller 7.

The flywheel cam 12 is mounted on a shaft 13 which is journalled to the frame and which is driven at constant speed by suitable motor means not shown.

Adjustable roller 46 is provided to adjust the length of the web between the dies 25, 26, and the knife 50. Roller 46 is mounted in adjustment slot 47 in the frame members. Idler roller 48 is journalled to the frame members just preceding the adjustable roller 46. i

The adjustments of the speed of roller 3, the travel of roller 7 and the adjustment of roller 46 are necessary to adjust for different length blanks. External drive means, not shown, are connected to overdrive the output roller 22 through a slip clutch 23 to maintain tension on the web at all times. Alternatively, roller 22 and slip clutch 23 may be connected to input drive shaft 13 by suitable gearing. A spring loaded pressure roller 24 is pivotally mounted on and between the frames and bears the output roller 22. Y

The first work station is illustrated as a punch and die set comprising a lower die and an upper die 26 which is connected to shaft 27 in block 28 which slides in gibs (not shown) connected to the frame. The block 28 is pivotally connected to connecting rod 32 and is driven through connecting rod 32 by a pair of crank arms 30 and 31rnounted on the main drive shaft. The main drive shaft 13 continues over and is journalled to the frame F The apparatus thus far described operates as follows:

The roller 3 pulls the strip at constant speed. The roller 7 oscillates up and down and manipulates the slack loop in the strip so that the motion of the strip past the work station is intermittent but has an average speed equal to the input speed. This arrangement permits high speed operation since the only thing that is intermittently varied in speed is the strip which has negligible Weight. All of the relatively heavy apparatus moves at constant or smoothly varying speed.

The strip, is taken away by the driven roller 22 bearing against the pressure roller 24 at a speed sufficient to maintain tension on the, web. at all times. The strip movement by the roller 22 is intermittent since it operates through the slip, clutch 23.

The adjustable knife is pivotally mounted on bearings in frame bracket members 51 and 52 which are rotatably adjustable on the frame plate 53 by means of the curved slot 54 in the holder member 52 and a corresponding slot in the holder 51. The knife 50 is adapted to be reciprocated by means of the member 38. Member 38 is reciprocated by the linkage comprising arm 39 fixedly mounted on shaft 40, which is journalled to the frame, and cam follower 39' riding on cam 41 which is mounted on shaft 13; The knife 50. cuts the web when the web is stationary against the stationary knife member 55 which is connected to the holder members 51 and 52.

FIGURE 2 is a schematic plan view of the web handling means. The-web 1 is fed in the direction of the arrow to the knife, 50. The web has been previously notched and punched with equal spacing by the reciprocating die as described in connection with FIGURE 1.

' It is desired to feed the blanks into the takeaway conveyor belts comprising lower belts and 61 and upper belts 62 and 63, the takeaway conveyor belts having fixed angular relation to the axis of the web motion. There- 45 fore, when the Web blank size is changed by rotating the knife. 50 it is necessary to change the' twisting angle through which the blanks are turned. The blanks are twisted by means of the cone rollers 64 and 65 mounted on the shaft 66. The cone rollers are designed to grasp the blank at the instant it is cut by the knife 50. Therefore, the upper cone rollers 64 and 65 are cut away (FIG- URE 5) so as not to interfere with the leading edge of the web which extends past the axis of the shaft 66 before the cutting takes place. Lower cone rollers 64 65;, may be solid.

The cone rollers twist the blank illustrated by the dotted line 67 through an angle sufiicient to line up the blanks symmetrically along the fixed position conveyor belts. Different angles of twist for different size blanks are provided by means of different size cone rollers, as will be discussed.

The blanks are then fed to the upper feed rollers 70 and 71 and lower rollers 70" and 71 with continuous positive control, that i the blanks are under the positive grasp of the feed rollers at all times. Due to the fact that the leading edge of the blank would interfere with the rollers 70, 71, if they were solid, these rollers are sectored so that only about half their surface comes in contact with the blanks, as in FIGURE 5A. The sector rollers are adjusted on their drive shaft to grip the blanks at the proper instant.

The blanks are then fed to a vacuum wheel 72 and then to the conveyor belts comprising the lower belts 6t) and 4 61 and the upper belts 62 and 63. By choosing the speed of the belts in relation ot the web feed blanks may be fed in a predetermined overlapping relation so that the flaps may be gummed or printing operations may be performed 5 on the blanks without any intermediate stacking or han- 1 which is suspended on mounting bar 129,, on frame members F and F The shaft 66 is driven by means of the shaft 66A mounted in the frame adapter 59 and connected to the shaft 66 by means of the universal joint 66b. Adapter 2 59 is connected to frame F by bolt 58.

The sector rollers 70 and 71 are mounted on the shaft 75, one end of which is mounted in the bracket 42 by means of the bearing 77. Bracket 42 is adjustably mounted on frame F by bolt 43. The other end of shaft 75 is 25 mounted in bracket 44 by bearing 76. Bracket 44 is adjustably mounted on frame R; by bolt 45. The rollers 70 and 71 are not full rollers but are cut away so that they have contact through approximately one half of their periphery as illustrated in FIGURE 5A. The lower 30 rollers 71 on shaft 75' may be full rollers.

The blanks are then fed from the sector rollers to the vacuum wheel 72 mounted on the shaft which is drivably mounted on the, frame F4 by bearing 79 and in frame F by bearing 78. A pair of guide rollers 81 and 82 are 35 also mounted on the shaft 80 in parallel relation to the vacuum roller 72. Vacuum is applied to the vacuum wheel 72 by means of the vacuum tube 83 which is connected to a source of vacuum and through valve 84 and the radial slot 85. A plurality of slots 85 are provided 40 depending upon the size of the blanks.

The valve comprises a pair of split blocks 84 and 84' FIGURE 6, which are bolted around the shaft 80 with suitable bearings. The block 84 contains an arcuate slot 86 which connects with the radial shaftways 85 in the wheel 72 to provide the vacuum. The timing of the vacuum may be controlled by rotating the valve blocks 84 and 84' around shaft 80. The valve position may be indexed by means of the forked arm 112, which engages the pin 109 mounted on the valve block 84. When the valve is properly indexed the setting is secured by means of the bolt 112a which secures the arm 112 to the frame.

FIGURE 6 shows a side view of FIGURE 4. The input drive may be connected to the gear and then to gear 96 mounted on shaft 660 which is mounted on the adapter 59 by means of bearings 97 and 98. The gear a 99 fixedly mounted on the shaft 66a drives gear 100 on shaft 75 to transmit power to the shaft 75 which drives the sector rollers. The gear 101, also mounted on shaft 75, drives gears 102 and 76' mounted on shaft 75' which drives the lower rollers which contacts the sector rollers.

Gear 76v also drives gears 147 and shaft 146 which drives the lower cone rollers, FIGURE 8.

It is necessary to make an accurate adjustment of the spacing between the upper and lower sector rollers 71 and 71 which means are as follows:

The lower sector roller 71 is mounted on shaft 75' which is mounted in fixed position on the frame. The upper sector roller 71 is mounted on shaft 75 and the spacing between the rollers is adjustable since the shaft 75 is mounted on the bracket 42 which is pivotally mounted to the frame by the bolt 43. The adjustment is made by means of the bolt 103 which extends through the bracket 104 connected to the frame. The lower end of the bolt 103 has threads 103 which are threaded into a 75 tapped hole in the bracket 42 and locked by locking screw 42a deforming slot 42b. A spring 106 is mounted around the bolt 103 and a threaded sleeve 107 is threaded into bracket 104 for the purpose of adjusting the spring pressure on the pivotally mounted bracket 42. The adjustments are made by first adjusting the spacing between the sector rollers on shaft and 75' by means of adjusting the bolt 103 with respect to the bracket 104, and looking with screw 42a. The spring pressure is then adjusted by adjusting the threaded sleeve 107 which is threaded into bracket 104.

The power for the vacuum wheel shaft is transmitted from the gear 108 on shaft 75 through the idler gear 110 mounted on the frame to the gear 111 on the shaft 80. The shaft 89 drives the vacuum wheel 72. Also mounted on the shaft 80 is the valve member 84, having the circular slot 86. The valve member 84 is clamped around the shaft by means of the shaft by means of the clamp 84 and the position of the slot 86 may be adjusted by rotation of the forked arm 112 which is adjustably mounted on a frame bracket and which contains a fork 112 at its lower end which engages the pin 109 on the valve bracket 84'. Therefore, by adjusting the position of the arm 112, the phasing of the vacuum control on the wheel 72 may be adjusted.

Referring to FIGURE 7 the blanks B are fed around the vacuum wheel 72 and guided by the guides 90-93 (also see FIGURE 3) onto the lower driven belt 61 which is mounted on the shaft 61' and then into contact with the upper driven belt 63 which is mounted on the roller shaft 63'. The upper and lower belts are geared together by gears not shown, and driven by the chain 63a connected to the sprockets 63b. The belts are driven at the same speed and the speed of the belts is chosen in relation to the speed of the vacuum wheel 72 so that the blanks may be placed between the conveyor belts in a predetermined overlapping relation or with any desired spacing. The blanks are under continuous positive control from the instant of being severed from the web until they are placed between the takeaway belts so that positive registration of the blanks is under control at all times.

FIGURE 8 shows a detail elevation view of the cone rollers and FIGURE 9 shows a detail top view of the cone roller mounting 128. The upper cone rollers comprise an outer set of rollers 64 and 65 which are cut away as illustrated in FIGURE 5. The rollers 64 and 65 are fixedly mounted on a connecting cylinder 117 which is fixedly mounted on the shaft 66 by means of set screws and 116. An inner set of cutaway cone rollers 64' and 65' are mounted on connecting half cylindrical half shell 120 and adapted to be adjustably clamped onto the cylinder body 117 of the outer rollers by means of the half shell clamp 121 and set screws 122 and 123. The purpose of having the inner set of cone rollers adjustably mounted with respect to the outer set is so that the contact periphery of the cone may be adjusted very accurately for the proper amount of twist.

The shaft 66 is mounted in bearings 124 and 125 which are mounted in spring loaded plates 126 and 127 which are slidably motmted in gibs 126' and 127 in the mounting bracket 128 is bolted to crossbar 129 which is connected to the side frame members F and F (FIGURE 3) so that the upper roller bracket 128 is suspended from above, this enables the blanks B to extend out either side. Adjustable spacing and adjustable spring pressure are provided for the upper cone rollers by means of the bolts 130 and 131 which are threaded at their lower end into the slidable blocks 126 and 127, the bolts being mounted in the brackets 130' and 131'. Adjustable spring pressure is provided by means of the springs 130a and 131a, which are acted upon by the adjustable threaded sleeves 1301) and 131b which are threaded into the brackets 130 and 131'. Locking means similar to 42a and 42b may be provided.

The drive to shaft 66 is provided by an input shaft 66A which is connected to an adjustment block 132. Power '6 is transmitted from the adjustment block to the gear 133 by means of the pin 134 in the gear 133.

In order for the rollers to seize the blank at the instant it is cut, a micrometer adjustment of the phasing is provided by the adjustment screws 135, and 136, FIGURE 8A, which are threaded into the block 132 to make a very fine phase adjustment of the gear 133 and the upper rollers relative to the cutting of the blank. The gear 133 is mounted on the shaft 133' which is mounted in the bearing 133a also mounted on the sliding block 127. The gear 133 meshes with the gear 137 mounted on the shaft 66.

The lower cone rollers 64a and 65a are mounted on shaft 141 which is journalled to the frame. The drive for the lower cone rollers is provided by means of the gears 142 mounted on the shaft 141 and which meshes with the gear 143 mounted on the input shaft 144 which is connected through a universal joint 145 to the drive shaft 146.

FIGURE 10 shows a diagram illustrating how different size blanks are inserted in the apparatus. Dashed line A shows the fixed line of the takeaway conveyor belt system. Dashed line B shows the arc of twisting movement of the blanks. The blank C shows a typical large envelope blank and the blank D shows a typical smaller envelope blank. These blanks are cut from webs being fed along the direction shown by the arrow B.

In order to obtain the proper twisting angle the center line of the web must be adjusted so that the leading points C and D of the respective blanks fall along the arc B so that when the cone rollers 64 and 65 grip the blanks they are turned so that their leading points follow the arc B to the point F and no further. At the point F the blanks are gripped by the rollers 70 and 71, FIGURE 2. Therefore, the different size blanks require different amounts of twisting which is provided by the adjustment of the contact area of the cone rollers. The phasing of the cone rollers must also be adjusted so that they grip the blank as it is cut by the knife 50 so the positive control is maintained at all times. In order to take care of the difference in web length the adjustment roller 46 is provided as well as the adjustments of the support of roller 3 and the movement of idler roller 7, FIGURE 1.

Note that the pivot point 0 of the knife 50 is fixed so that the web must be adjusted relative to it.

Many modifications may be made by those who desire to practice the invention without departing from the scope thereof which is defined by the following claims.

We claim:

1. Means for making different size envelope blanks comprising:

a frame,

input means to feed a web at adjustable constant speed comprising,

driven roller means and means to adjust the speed of said driven roller,

means to provide intermittent motion of said web at a reciprocating punch station comprising,

input and output idler rollers adapted to maintain the plane of said web through said punch station,

an oscillating roller located between said driven roller means and said input idler roller means,

said driven rollers being located directly before said oscillating roller to minimize the load on said oscillating roller,

means to oscillate said oscillating roller comprising,

a pair of arms pivotally mounted to the frame,

an adjustable linkage connected to said arms and means to oscillate said adjustable linkage,

and means to adjust said linkage to vary said oscillation of said oscillating roller,

reciprocating means for punching said web at said work station when said web is stationary,

overdriven roller means to move said web from said work station with intermittent motion,

adjustable angle reciprocating knife means spaced a predetermined distance in the direction of web movement from said work station for thereafter severing said Web while said web is stationary,

adjustable web takeup means between said punching means and said knife to thereby provide adjustable size envelope blanks, and adjustable cone roller means to remove said different size blanks to a fixed location takeaway means.

2. Means [for making different size envelope blanks comprising:

a frame,

input means to feed a web at adjustable constant speed comprising,

driven roller means, and means to adjust the speed of said driven roller,

means to provide intermittent motion of said web at a reciprocating punch station comprising,

input and output idler rollers adapted to maintain the plane of said web through said punch station,

an oscillating roller located between said driven roller means and said input idler roller means,

means to oscillate said oscillating roller comprising,

said driven rollers being located directly before said oscillating roller to minimize the load on said oscillating roller,

a pair of arms pivotally mounted to the frame,

an adjustable linkage connected to said arms and means to oscillate said adjustable linkage, V

and means to adjust said linkage to vary said oscillation of said oscillating roller,

reciprocating means for punching said web at said work station when said Web is stationary,

adjustable angle reciprocating knife means spaced a predetermined distance in the direction of Web movement from said work station for thereafter severing said web while said Web is stationary,

adjustable web takeup means between said punching means and said knife to thereby provide adjustable size enevlope blanks, and adjustable cone roller means to remove said different size blanks to a fixed location takeaway means.

' 3. Means for making different size envelope blanks comprising:

8 a frame, input means to feed a web at adjustable constant speed comprising,

driven roller means, and means to adjust the speed of said driven roller,

means to provide intermittent motion of said web at a reciprocating punch station comprising,

input and output idler rollers adapted to maintain the plane of said web through said punch station,

an oscillating roller located between said driven roller means and said input idler roller means,

said driven rollers being located directly before said oscillating roller to minimize the load on said oscillating roller,

means to oscillate said oscillating roller comprising,

a pair of arms pivotally mounted to the frame,

an adjustable linkage connected to said arms and means to oscillate said adjustable linkage,

and means to adjust said linkage to vary said oscillation of said oscillating roller,

reciprocating means for punching said web at said work station when said web is stationary,

adjustable angle reciprocatin g knife means spaced a predetermined distance in the direction of web movement from said Work station for thereafter severing said web while said web is stationary, to thereby provide adjustable size envelope blanks,

and adjustable cone roller means to remove said different size blanks to a fixed location takeaway means.

References Cited by the Examiner UNITED STATES PATENTS WILLIAM W. DYER, JR., Primary Examiner. LEON PEAR, Examiner.

L. B. TAYLOR, Assistant Examiner. 

1. MEANS FOR MAKING DIFFERENT SIZE ENVELOPE BLANKS COMPRISING: A FRAME, INPUT MEANS TO FEED A WEB AT ADJUSTABLE CONSTANT SPEED COMPRISING, DRIVEN ROLLER MEANS AND MEANS TO ADJUST THE SPEED OF SAID DRIVEN ROLLER, MEANS TO PROVIDE INTERMITTENT MOTION OF SAID WEB AT A RECIPROCATING PUNCH STATION COMPRISING, INPUT AND OUTPUT IDLER ROLLERS ADAPTED TO MAINTAIN THE PLANE OF SAID WEB THROUGH SAID PUNCH STATION, AN OSCILLATING ROLLER LOCATED BETWEEN SAID DRIVEN ROLLER MEANS AND SAID INPUT IDLER ROLLER MEANS, SAID DRIVEN ROLLERS BEING LOCATED DIRECTLY BEFORE SAID OSCILLATING ROLLER TO MINIMIZE THE LOAD ON SAID OSCILLATING ROLLER, MEANS TO OSCILLATE SAID OSCILLATING ROLLER COMPRISING, A PAIR OF ARMS PIVOTALLY MOUNTED TO THE FRAME, AN ADJUSTABLE LINKAGE CONNECTED TO SAID ARMS AND MEANS TO OSCILLATE SAID ADJUSTABLE LINKAGE, AND MEANS TO ADJUST SAID LINKAGE TO VARY SAID OSCILLATION OF SAID OSCILLATION ROLLER, RECIPROCATING MEANS FOR PUNCHING SAID WEB AT SAID WORK STATION WHEN SAID WEB IS STATIONARY, OVERDRIVEN ROLLER MEANS TO MOVE SAID WEB FROM SAID WORK STATION WITH INTERMITTENT MOTION, ADJUSTABLE ANGLE RECIPROCATING KNIFE MEANS SPACED A PREDETERMINED DISTANCE IN THE DIRECTION OF WEB MOVEMENT FROM SAID WORK STATION FOR THEREAFTER SEVERING SAID WEB WHILE SAID WEB IS STATIONARY, ADJUSTABLE WEB TAKEUP MEANS BETWEEN SAID PUNCHING MEANS AND SAID KNIFE TO THEREBY PROVIDE ADJUSTABLE SIZE ENVELOPE BLANKS, AND ADJUSTABLE CONE ROLLER MEANS TO REMOVE SAID DIFFERENT SIZE BLANKS TO A FIXED LOCATION TAKEAWAY MEANS. 